US20070199725A1 - Pressure-Fluid-Operated Percussion Device - Google Patents
Pressure-Fluid-Operated Percussion Device Download PDFInfo
- Publication number
- US20070199725A1 US20070199725A1 US10/590,205 US59020505A US2007199725A1 US 20070199725 A1 US20070199725 A1 US 20070199725A1 US 59020505 A US59020505 A US 59020505A US 2007199725 A1 US2007199725 A1 US 2007199725A1
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- United States
- Prior art keywords
- pressure
- pressure liquid
- pressure chamber
- tool
- working
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000009527 percussion Methods 0.000 title claims abstract description 52
- 239000007788 liquid Substances 0.000 claims abstract description 63
- 230000005540 biological transmission Effects 0.000 claims abstract description 45
- 239000000463 material Substances 0.000 description 12
- 230000001133 acceleration Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 2
- 239000011435 rock Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B1/00—Percussion drilling
- E21B1/36—Tool-carrier piston type, i.e. in which the tool is connected to an impulse member
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/06—Means for driving the impulse member
- B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D9/14—Control devices for the reciprocating piston
- B25D9/16—Valve arrangements therefor
- B25D9/18—Valve arrangements therefor involving a piston-type slide valve
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2209/00—Details of portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
- B25D2209/002—Pressure accumulators
Definitions
- the invention relates to a pressure-fluid-operated percussion device comprising a frame allowing a tool to be arranged therein movably in its longitudinal direction, means for feeding pressure liquid to the percussion device and for returning pressure liquid to a pressure liquid tank, and means for producing a stress pulse in the tool by utilizing pressure of the pressure liquid, wherein the percussion device comprises a working pressure chamber filled with pressure liquid and, between the working pressure chamber and the tool, a transmission piston which is movably arranged in the longitudinal direction of the frame and which is in contact with the tool either directly or indirectly at least during stress pulse generation, and a charging pressure chamber on the side of the transmission piston facing the tool so that the transmission piston is provided with a pressure surface facing the working pressure chamber and on the side of the charging pressure chamber a pressure surface facing the tool.
- a stress pulse in a tool is produced by using a reciprocating percussion piston which, at the end of its stroke movement, hits an end of a tool or a shank connected thereto, thus producing in the tool a stress pulse propagating towards the material to be processed.
- the reciprocating stroke movement of a percussion piston is typically produced by means of a pressure medium whose pressure makes the percussion piston move in at least one direction, today typically in both directions.
- a pressure accumulator or a spring or the like may be utilized to store energy during a return movement.
- An object of the present invention is to provide a percussion device to enable dynamic forces generated therein and drawbacks caused thereby to become significantly smaller.
- a further object is to provide a percussion device which has a good efficiency and which enables stress pulse frequencies significantly higher than existing ones to be provided.
- the percussion device of the invention is characterized in that the means for producing a stress pulse comprise a pressure liquid source connected with the working pressure chamber in order to maintain pressure in the working pressure chamber, and means for intermittently feeding, to the charging pressure chamber, pressure liquid whose pressure enables the transmission piston to be pushed towards the working pressure chamber, against the pressure of the pressure liquid in the working pressure chamber and into a predetermined backward position of the transmission piston such that pressure liquid is discharged from the working pressure chamber, and for alternately allowing pressure liquid to be discharged rapidly from the charging pressure chamber so that a force produced by the pressure of the pressurized pressure liquid in the working pressure chamber and flowing thereto from the pressure liquid source pushes the transmission piston in the direction of the tool, compressing the tool in its longitudinal direction and thus generating a stress pulse in the tool.
- the means for producing a stress pulse comprise a pressure liquid source connected with the working pressure chamber in order to maintain pressure in the working pressure chamber, and means for intermittently feeding, to the charging pressure chamber, pressure liquid whose pressure enables the transmission piston to be
- a basic idea underlying the invention is that the transmission piston is continuously subjected to a pressure acting towards the tool, the pressure being derived from a pressure fluid source connected to the working pressure chamber.
- a further basic idea underlying the invention is that pressurized pressure fluid is fed to a charging pressure chamber residing on another side of the transmission piston to move the transmission piston to a particular predetermined position, i.e. to a position wherefrom the transmission piston is allowed, by means of a force produced by the pressure in the working chamber, to abruptly compress the tool towards the material to be processed, thus producing a stress pulse in the tool.
- Still another basic idea underlying the invention is that when the transmission piston is in said position and substantially in contact with the tool or shank, the charging pressure chamber is connected with a “tank pressure” so that the pressure acting on the opposite side of the transmission piston produces a sudden compression on the tool or the like, thus producing a stress pulse which propagates through the tool to the material to be processed.
- An advantage of the invention is that this solution enables a good efficiency to be achieved since moving the transmission piston to a stress pulse initiating position, i.e. to a releasing position, takes place substantially against a constant pressure.
- a further advantage of the invention is that this enables the compressive stress energy of a stress wave being reflected from the material being processed via the tool and the transmission piston to the working pressure chamber to be recovered.
- the stress pulse generation frequency can be made considerably higher than that of the known percussion devices since there is no large-mass, and thus slow, percussion piston which is to be made to reciprocate.
- Still another advantage of the invention is that the solution is simple to implement and the operation is easy to control.
- FIGS. 1 a and 1 b show principles of an embodiment of a percussion device according to the invention during charging and during stress pulse generation, respectively, and
- FIGS. 2 a and 2 b show theoretical energy graphs related to charging and stress pulse generation, respectively.
- FIG. 1 a schematically shows principles of an embodiment of a percussion device according to the invention in a situation wherein the percussion device is being “charged” in order to produce a stress pulse.
- the figure shows a percussion device 1 comprising a frame 2 .
- the frame comprises a working pressure chamber 3 which, on one side, is defined by a transmission piston 4 .
- the working pressure chamber 3 is connected via a channel 5 to a pressure source, such as a pressure liquid pump 6 , which feeds pressurized pressure liquid to the space 3 at a pressure P 1 .
- a charging pressure chamber 7 is provided which, in turn, is connected via a channel 8 and a valve 9 to a pressure liquid source, such as a pressure liquid pump 10 , which feeds pressurized liquid whose pressure is P 2 .
- a pressure liquid return channel 11 is further provided to a pressure liquid tank 12 .
- a tool 13 which may be a drill rod or, typically, a shank connected to the drill rod, is further connected to the percussion device 1 .
- a drill bit such as a rock bit or the like, not shown, which during operation is in contact with the material to be processed. It may further comprise a pressure accumulator 14 connected with the working pressure chamber 3 in order to dampen pressure pulses.
- “charging” is implemented wherein pressure liquid, controlled by the valve 9 , is fed to the charging pressure chamber 7 such that the transmission piston 4 moves in the direction of arrow A until it has settled, in the position according to FIG. 1 a, in its uppermost, i.e. backward, position. At the same time pressure liquid is discharged from the working pressure chamber.
- the backward position of the transmission piston 4 is determined by the mechanical solutions in the percussion device 1 , such as various shoulders or stops; in the embodiment according to FIGS. 1 a and 1 b, a shoulder 2 a and the rear surface of a flange 4 a of the transmission piston.
- the percussion device 1 is pushed towards the material to be processed at force F, i.e. a “feed force”, which keeps the transmission piston 4 in contact with the tool 13 and the tip thereof, i.e. a drill bit or the like, in contact with the material to be processed.
- force F i.e. a “feed force”
- the transmission piston 4 has moved in the direction of arrow A as far as possible, the valve 9 is moved into the position shown in FIG. 1 b so that pressure liquid from the charging pressure chamber 7 is allowed to abruptly discharge into the pressure liquid tank 12 .
- the transmission piston is then allowed to move forward in the direction of the tool 13 due to the pressure of the pressure liquid in the working pressure chamber 3 and further flowing thereto from the pressure liquid pump 6 .
- Pressure P 1 acting on the transmission piston 4 in the working pressure chamber 3 produces a force which pushes the transmission piston 4 in the direction of arrow B towards the tool 13 , compressing the tool 13 .
- a sudden compressive stress is generated in the tool 13 through the transmission piston 4 , this sudden compressive stress thus producing a stress pulse through the tool 13 all the way to the material to be processed.
- a “reflection pulse” being reflected from the material being processed returns through the tool 13 , pushing the transmission piston 4 again in the direction of arrow A in FIG. 1 a so that the energy of the stress pulse is transferred to the pressure liquid in the working pressure chamber.
- the valve 9 is again switched to the position shown in FIG. 1 a, and pressure liquid is again fed to the charging chamber 7 to push the transmission piston 4 to its predetermined backward position.
- Pressure surface areas of the transmission piston 4 i.e. a surface area A 1 facing the working pressure chamber 3 and a surface area A 2 facing the charging chamber 7 , respectively, can be chosen in many different ways.
- the simplest way of implementation is the embodiment shown in FIGS. 1 a and 1 b wherein the surface areas differ in size.
- choosing the surface areas appropriately enables pressures of equal amount to be used on both sides of the transmission piston 4 , i.e. pressures P 1 and P 2 may be equal in amount. Therefore, pressure liquid may enter both spaces from the same pressure liquid source. This simplifies the implementation of the percussion device.
- the transmission piston 4 may readily be provided with a shoulder-like flange 4 a and the frame may readily be provided with a shoulder 2 a, respectively, so that the shoulder 2 a of the frame 2 defines the backward position of the transmission piston 4 ; in the figure the uppermost position, i.e. position where stress pulse generation always starts.
- the surface areas may also be equal in size, in which case pressure P 2 has to be higher than pressure P 1 .
- FIGS. 2 a and 2 b describe theoretical energy graphs related to charging and stress pulse generation, respectively, in a percussion device according to the invention.
- the amount of energy transferred to a stress pulse is P 1 ⁇ V 1 , i.e. the product of pressure and said volume, which is depicted by rectangle D. If the value of the pressure acting in the working chamber would be 0 at the end, the amount of energy transferred to a stress pulse would be P 1 ⁇ V 1 /2, i.e. half the energy mentioned above, which is depicted by triangle E.
- the percussion device Using short travels in the direction of a tool, the percussion device according to the invention enables stress pulses to be produced at a high frequency since the necessary amounts of pressure liquid to be fed are relatively small while they at the same time enable a large force to be produced. Furthermore, since the mass of the transmission piston 4 is small, no significant dynamic forces are generated. Similarly, moving the transmission piston 4 into its backward position, i.e. starting position, only requires a short movement, thus enabling pulses and a high stress pulse frequency to be achieved, which results in a high frequency of stress pulses between the tool and the material to be processed, usually also called a stroke frequency in connection with known percussion devices.
- the drawings and the related description are only intended to illustrate the idea of the invention. The details of the invention may vary within the scope of the claims.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Mining & Mineral Resources (AREA)
- Environmental & Geological Engineering (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Geochemistry & Mineralogy (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
- The invention relates to a pressure-fluid-operated percussion device comprising a frame allowing a tool to be arranged therein movably in its longitudinal direction, means for feeding pressure liquid to the percussion device and for returning pressure liquid to a pressure liquid tank, and means for producing a stress pulse in the tool by utilizing pressure of the pressure liquid, wherein the percussion device comprises a working pressure chamber filled with pressure liquid and, between the working pressure chamber and the tool, a transmission piston which is movably arranged in the longitudinal direction of the frame and which is in contact with the tool either directly or indirectly at least during stress pulse generation, and a charging pressure chamber on the side of the transmission piston facing the tool so that the transmission piston is provided with a pressure surface facing the working pressure chamber and on the side of the charging pressure chamber a pressure surface facing the tool.
- In the prior art, in a percussion device a stress pulse in a tool is produced by using a reciprocating percussion piston which, at the end of its stroke movement, hits an end of a tool or a shank connected thereto, thus producing in the tool a stress pulse propagating towards the material to be processed. The reciprocating stroke movement of a percussion piston is typically produced by means of a pressure medium whose pressure makes the percussion piston move in at least one direction, today typically in both directions. In order to enhance the stroke movement, a pressure accumulator or a spring or the like may be utilized to store energy during a return movement.
- Due to the reciprocating movement of a percussion piston, acceleration forces in opposite directions are alternately produced in percussion devices equipped with a percussion piston which subject the mechanism to stress and impede control of the percussion device. In addition, due to such forces, boom structures and feeding apparatuses usually employed for supporting a percussion device have to be more robust than would otherwise be necessary. Furthermore, in order to make a stress pulse to be transferred from the tool to the material to be processed, such as rock to be broken, efficiently enough, the percussion device, and hence the tool, have to be pushed against the material with a sufficient force. Due to dynamic acceleration forces, the feed force and structures, accordingly, have to be dimensioned to be robust enough so that the pressing force on the tool which remains as a difference of acceleration caused by the feed force and the movement of the percussion piston would still be sufficiently large. Furthermore, percussion devices equipped with a percussion piston operating by a reciprocating stroke movement are only able to provide low stroke frequencies since to accelerate the percussion piston in its direction of movement always requires an amount of power proportional to the mass of the percussion piston, and high frequencies would require high acceleration and thus extremely high powers. This, in turn, is not feasible in practice, since all the rest in the percussion device and the support structure thereof would have to be dimensioned accordingly. When at the same time this would result in a considerable decrease in efficiency, the stroke frequency of existing percussion devices is only a few dozens of Hz at its best.
- An object of the present invention is to provide a percussion device to enable dynamic forces generated therein and drawbacks caused thereby to become significantly smaller. A further object is to provide a percussion device which has a good efficiency and which enables stress pulse frequencies significantly higher than existing ones to be provided.
- The percussion device of the invention is characterized in that the means for producing a stress pulse comprise a pressure liquid source connected with the working pressure chamber in order to maintain pressure in the working pressure chamber, and means for intermittently feeding, to the charging pressure chamber, pressure liquid whose pressure enables the transmission piston to be pushed towards the working pressure chamber, against the pressure of the pressure liquid in the working pressure chamber and into a predetermined backward position of the transmission piston such that pressure liquid is discharged from the working pressure chamber, and for alternately allowing pressure liquid to be discharged rapidly from the charging pressure chamber so that a force produced by the pressure of the pressurized pressure liquid in the working pressure chamber and flowing thereto from the pressure liquid source pushes the transmission piston in the direction of the tool, compressing the tool in its longitudinal direction and thus generating a stress pulse in the tool.
- A basic idea underlying the invention is that the transmission piston is continuously subjected to a pressure acting towards the tool, the pressure being derived from a pressure fluid source connected to the working pressure chamber.
- A further basic idea underlying the invention is that pressurized pressure fluid is fed to a charging pressure chamber residing on another side of the transmission piston to move the transmission piston to a particular predetermined position, i.e. to a position wherefrom the transmission piston is allowed, by means of a force produced by the pressure in the working chamber, to abruptly compress the tool towards the material to be processed, thus producing a stress pulse in the tool.
- Still another basic idea underlying the invention is that when the transmission piston is in said position and substantially in contact with the tool or shank, the charging pressure chamber is connected with a “tank pressure” so that the pressure acting on the opposite side of the transmission piston produces a sudden compression on the tool or the like, thus producing a stress pulse which propagates through the tool to the material to be processed.
- An advantage of the invention is that this solution enables a good efficiency to be achieved since moving the transmission piston to a stress pulse initiating position, i.e. to a releasing position, takes place substantially against a constant pressure. A further advantage of the invention is that this enables the compressive stress energy of a stress wave being reflected from the material being processed via the tool and the transmission piston to the working pressure chamber to be recovered. A still further advantage is that the stress pulse generation frequency can be made considerably higher than that of the known percussion devices since there is no large-mass, and thus slow, percussion piston which is to be made to reciprocate. Still another advantage of the invention is that the solution is simple to implement and the operation is easy to control.
- The invention will be described in closer detail in the accompanying drawings, wherein
-
FIGS. 1 a and 1 b show principles of an embodiment of a percussion device according to the invention during charging and during stress pulse generation, respectively, and -
FIGS. 2 a and 2 b show theoretical energy graphs related to charging and stress pulse generation, respectively. -
FIG. 1 a schematically shows principles of an embodiment of a percussion device according to the invention in a situation wherein the percussion device is being “charged” in order to produce a stress pulse. The figure shows apercussion device 1 comprising aframe 2. For pressure liquid, the frame comprises aworking pressure chamber 3 which, on one side, is defined by atransmission piston 4. Theworking pressure chamber 3 is connected via achannel 5 to a pressure source, such as apressure liquid pump 6, which feeds pressurized pressure liquid to thespace 3 at a pressure P1. On the other side of thetransmission piston 4, opposite to thepressure chamber 3, acharging pressure chamber 7 is provided which, in turn, is connected via achannel 8 and avalve 9 to a pressure liquid source, such as apressure liquid pump 10, which feeds pressurized liquid whose pressure is P2. From thevalve 9, a pressureliquid return channel 11 is further provided to apressure liquid tank 12. - A
tool 13, which may be a drill rod or, typically, a shank connected to the drill rod, is further connected to thepercussion device 1. At the opposite end of the tool, there is provided a drill bit, such as a rock bit or the like, not shown, which during operation is in contact with the material to be processed. It may further comprise apressure accumulator 14 connected with theworking pressure chamber 3 in order to dampen pressure pulses. - In the situation shown in
FIG. 1 a, “charging” is implemented wherein pressure liquid, controlled by thevalve 9, is fed to thecharging pressure chamber 7 such that thetransmission piston 4 moves in the direction of arrow A until it has settled, in the position according toFIG. 1 a, in its uppermost, i.e. backward, position. At the same time pressure liquid is discharged from the working pressure chamber. The backward position of thetransmission piston 4 is determined by the mechanical solutions in thepercussion device 1, such as various shoulders or stops; in the embodiment according toFIGS. 1 a and 1 b, ashoulder 2 a and the rear surface of aflange 4 a of the transmission piston. During operation of the percussion device, thepercussion device 1 is pushed towards the material to be processed at force F, i.e. a “feed force”, which keeps thetransmission piston 4 in contact with thetool 13 and the tip thereof, i.e. a drill bit or the like, in contact with the material to be processed. When thetransmission piston 4 has moved in the direction of arrow A as far as possible, thevalve 9 is moved into the position shown inFIG. 1 b so that pressure liquid from thecharging pressure chamber 7 is allowed to abruptly discharge into thepressure liquid tank 12. The transmission piston is then allowed to move forward in the direction of thetool 13 due to the pressure of the pressure liquid in theworking pressure chamber 3 and further flowing thereto from thepressure liquid pump 6. Pressure P1 acting on thetransmission piston 4 in theworking pressure chamber 3 produces a force which pushes thetransmission piston 4 in the direction of arrow B towards thetool 13, compressing thetool 13. As a result, a sudden compressive stress is generated in thetool 13 through thetransmission piston 4, this sudden compressive stress thus producing a stress pulse through thetool 13 all the way to the material to be processed. A “reflection pulse” being reflected from the material being processed, in turn, returns through thetool 13, pushing thetransmission piston 4 again in the direction of arrow A inFIG. 1 a so that the energy of the stress pulse is transferred to the pressure liquid in the working pressure chamber. At the same time, thevalve 9 is again switched to the position shown inFIG. 1 a, and pressure liquid is again fed to thecharging chamber 7 to push thetransmission piston 4 to its predetermined backward position. - Pressure surface areas of the
transmission piston 4, i.e. a surface area A1 facing theworking pressure chamber 3 and a surface area A2 facing thecharging chamber 7, respectively, can be chosen in many different ways. The simplest way of implementation is the embodiment shown inFIGS. 1 a and 1 b wherein the surface areas differ in size. In such a case, choosing the surface areas appropriately enables pressures of equal amount to be used on both sides of thetransmission piston 4, i.e. pressures P1 and P2 may be equal in amount. Therefore, pressure liquid may enter both spaces from the same pressure liquid source. This simplifies the implementation of the percussion device. This, in turn, results in a further advantage that thetransmission piston 4 may readily be provided with a shoulder-like flange 4 a and the frame may readily be provided with ashoulder 2 a, respectively, so that theshoulder 2 a of theframe 2 defines the backward position of thetransmission piston 4; in the figure the uppermost position, i.e. position where stress pulse generation always starts. The surface areas may also be equal in size, in which case pressure P2 has to be higher than pressure P1. -
FIGS. 2 a and 2 b describe theoretical energy graphs related to charging and stress pulse generation, respectively, in a percussion device according to the invention. - When the transmission piston is moved according to
FIG. 2 a against pressure P1 acting in the working pressure chamber, at the end the amount of charged energy is P1×V1, i.e. the product of pressure and volume replaced by a pressure area A1, which is depicted by rectangle A. If the value of the pressure acting in the working pressure chamber would initially be 0, the amount of charged energy would be P1×V1/2, i.e. half the energy mentioned above, which is depicted by triangle B. Similarly, the amount of energy fed into the percussion device is depicted by rectangle C shown in broken line, which is the product of pressure P2 (substantially constant) and an increase in volume V2 that has occurred as a result of a transition of a pressure surface A2. This surface area of rectangle C, i.e. the fed energy, is equal in size to the surface area of rectangle A. - When the transmission piston is according to
FIG. 2 b allowed to press the tool, the amount of energy transferred to a stress pulse is P1×V1, i.e. the product of pressure and said volume, which is depicted by rectangle D. If the value of the pressure acting in the working chamber would be 0 at the end, the amount of energy transferred to a stress pulse would be P1×V1/2, i.e. half the energy mentioned above, which is depicted by triangle E. - Although this theoretical examination does not accurately depict real operational processes and pressure levels in practice, it nevertheless provides a clear description as to how the percussion device of the invention, by employing the same pressure values of pressure liquid to be fed, enables power higher than that produced by devices wherein the pressure varies between zero and a maximum pressure to be achieved.
- Using short travels in the direction of a tool, the percussion device according to the invention enables stress pulses to be produced at a high frequency since the necessary amounts of pressure liquid to be fed are relatively small while they at the same time enable a large force to be produced. Furthermore, since the mass of the
transmission piston 4 is small, no significant dynamic forces are generated. Similarly, moving thetransmission piston 4 into its backward position, i.e. starting position, only requires a short movement, thus enabling pulses and a high stress pulse frequency to be achieved, which results in a high frequency of stress pulses between the tool and the material to be processed, usually also called a stroke frequency in connection with known percussion devices. The drawings and the related description are only intended to illustrate the idea of the invention. The details of the invention may vary within the scope of the claims.
Claims (5)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FI20040278A FI116124B (en) | 2004-02-23 | 2004-02-23 | Impact fluid driven impactor |
FI20040278 | 2004-02-23 | ||
PCT/FI2005/050045 WO2005080051A1 (en) | 2004-02-23 | 2005-02-22 | Pressure-fluid-operated percussion device |
Publications (2)
Publication Number | Publication Date |
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US20070199725A1 true US20070199725A1 (en) | 2007-08-30 |
US7878263B2 US7878263B2 (en) | 2011-02-01 |
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/590,205 Expired - Fee Related US7878263B2 (en) | 2004-02-23 | 2005-02-22 | Pressure-fluid-operated percussion device |
Country Status (12)
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US (1) | US7878263B2 (en) |
EP (1) | EP1720685B1 (en) |
JP (1) | JP5009779B2 (en) |
CN (1) | CN100542753C (en) |
AU (1) | AU2005215178B8 (en) |
BR (1) | BRPI0507974A (en) |
CA (1) | CA2557060C (en) |
FI (1) | FI116124B (en) |
NO (1) | NO332788B1 (en) |
RU (1) | RU2353508C2 (en) |
WO (1) | WO2005080051A1 (en) |
ZA (1) | ZA200607006B (en) |
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US20060157259A1 (en) * | 2003-07-07 | 2006-07-20 | Markku Keskiniva | Impact device and method for generating stress pulse therein |
WO2017000015A1 (en) * | 2015-06-29 | 2017-01-05 | Brooke & Mackenzie Pty Ltd | Variable blow hydraulic hammer |
KR20180040646A (en) * | 2015-08-13 | 2018-04-20 | 하테부르 움포름마쉬넨 아크티엔게젤샤프트 | Apparatus and uses for generating impact-dynamic process forces |
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SE528654C2 (en) * | 2005-05-23 | 2007-01-09 | Atlas Copco Rock Drills Ab | Impulse generator for rock drill, comprises impulse piston housed inside chamber containing compressible liquid |
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SE530572C2 (en) * | 2006-11-16 | 2008-07-08 | Atlas Copco Rock Drills Ab | Pulse machine for a rock drill, method for creating mechanical pulses in the pulse machine, and rock drill and drill rig including such pulse machine |
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NO330266B1 (en) | 2009-05-27 | 2011-03-14 | Nbt As | Device using pressure transients for transport of fluids |
CA2801640A1 (en) | 2010-06-17 | 2011-12-22 | Impact Technology Systems As | Method employing pressure transients in hydrocarbon recovery operations |
US8733468B2 (en) * | 2010-12-02 | 2014-05-27 | Caterpillar Inc. | Sleeve/liner assembly and hydraulic hammer using same |
AR089304A1 (en) | 2011-12-19 | 2014-08-13 | Impact Technology Systems As | IMPACT PRESSURE RECOVERY METHOD |
SE536903C2 (en) * | 2012-11-28 | 2014-10-21 | Atlas Copco Rock Drills Ab | Device at distribution valve for a rock drill and rock drill |
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FI116125B (en) * | 2001-07-02 | 2005-09-30 | Sandvik Tamrock Oy | Type of device |
FI116513B (en) * | 2003-02-21 | 2005-12-15 | Sandvik Tamrock Oy | Type of device |
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2004
- 2004-02-23 FI FI20040278A patent/FI116124B/en not_active IP Right Cessation
-
2005
- 2005-02-22 AU AU2005215178A patent/AU2005215178B8/en not_active Ceased
- 2005-02-22 CN CNB2005800056951A patent/CN100542753C/en not_active Expired - Fee Related
- 2005-02-22 JP JP2007500240A patent/JP5009779B2/en not_active Expired - Fee Related
- 2005-02-22 RU RU2006133905/02A patent/RU2353508C2/en not_active IP Right Cessation
- 2005-02-22 EP EP05717299.1A patent/EP1720685B1/en not_active Not-in-force
- 2005-02-22 BR BRPI0507974-8A patent/BRPI0507974A/en not_active IP Right Cessation
- 2005-02-22 US US10/590,205 patent/US7878263B2/en not_active Expired - Fee Related
- 2005-02-22 WO PCT/FI2005/050045 patent/WO2005080051A1/en active Application Filing
- 2005-02-22 CA CA2557060A patent/CA2557060C/en not_active Expired - Fee Related
-
2006
- 2006-08-22 ZA ZA200607006A patent/ZA200607006B/en unknown
- 2006-09-19 NO NO20064244A patent/NO332788B1/en not_active IP Right Cessation
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US4688468A (en) * | 1982-06-08 | 1987-08-25 | Intreprinderea De Utilaj Greu "Progresul" | Method of and apparatus for controlling pulse hydraulic generators |
US4676323A (en) * | 1984-05-24 | 1987-06-30 | Atlas Copco Aktiebolag | Hydraulically operated percussive machine and an accumulator therefor |
US4852663A (en) * | 1985-03-26 | 1989-08-01 | The Steel Engineering Company Limited | Hydraulic percussive machines |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060157259A1 (en) * | 2003-07-07 | 2006-07-20 | Markku Keskiniva | Impact device and method for generating stress pulse therein |
US8151901B2 (en) * | 2003-07-07 | 2012-04-10 | Sandvik Mining And Construction Oy | Impact device and method for generating stress pulse therein |
WO2017000015A1 (en) * | 2015-06-29 | 2017-01-05 | Brooke & Mackenzie Pty Ltd | Variable blow hydraulic hammer |
AU2016286170B2 (en) * | 2015-06-29 | 2018-11-08 | Brooke And Mackenzie Pty Ltd | Variable blow hydraulic hammer |
KR20180040646A (en) * | 2015-08-13 | 2018-04-20 | 하테부르 움포름마쉬넨 아크티엔게젤샤프트 | Apparatus and uses for generating impact-dynamic process forces |
KR102533336B1 (en) * | 2015-08-13 | 2023-05-17 | 하테부르 움포름마쉬넨 아크티엔게젤샤프트 | Devices and applications for generating shock-dynamic process forces |
Also Published As
Publication number | Publication date |
---|---|
WO2005080051A8 (en) | 2005-10-27 |
US7878263B2 (en) | 2011-02-01 |
RU2353508C2 (en) | 2009-04-27 |
RU2006133905A (en) | 2008-03-27 |
NO332788B1 (en) | 2013-01-14 |
FI20040278A0 (en) | 2004-02-23 |
BRPI0507974A (en) | 2007-07-24 |
FI116124B (en) | 2005-09-30 |
AU2005215178B2 (en) | 2010-02-25 |
CA2557060C (en) | 2012-10-23 |
JP5009779B2 (en) | 2012-08-22 |
ZA200607006B (en) | 2007-12-27 |
CN100542753C (en) | 2009-09-23 |
EP1720685A1 (en) | 2006-11-15 |
AU2005215178A1 (en) | 2005-09-01 |
AU2005215178B8 (en) | 2010-06-24 |
NO20064244L (en) | 2006-09-19 |
WO2005080051A1 (en) | 2005-09-01 |
CA2557060A1 (en) | 2005-09-01 |
CN1921987A (en) | 2007-02-28 |
JP2007522954A (en) | 2007-08-16 |
EP1720685B1 (en) | 2015-08-19 |
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